WO2012089192A1 - Transmission à dérivation de puissance - Google Patents
Transmission à dérivation de puissance Download PDFInfo
- Publication number
- WO2012089192A1 WO2012089192A1 PCT/DE2011/002148 DE2011002148W WO2012089192A1 WO 2012089192 A1 WO2012089192 A1 WO 2012089192A1 DE 2011002148 W DE2011002148 W DE 2011002148W WO 2012089192 A1 WO2012089192 A1 WO 2012089192A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- transmission according
- gear
- hydraulic motor
- housing
- adaptive
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
- F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
- F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
- F16H39/02—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motors at a distance from liquid pumps
Definitions
- the invention relates to a hydrostatic mechanical power split transmission.
- a hydrostatic mechanical power split transmission is described for example in DE 10 2004 001 929 A1.
- a power split transmission with 'continuously variable transmission ratio having a hydrostatic transmission part, comprising a first hydrostatic unit with Cincinnatim volume and a second hydrostatic unit having a constant volume and a mechanical transmission part comprising a summation transmission and a range gearbox, wherein the summing gear and the range gear Off-axis to the hydrostatic units are arranged.
- a further hydrostatically mechanical line branching transmission is described in WO 2009/071060 A2, comprising a housing, respectively a housing composed of individual housing parts, at least one drive shaft which can be driven by at least one drive motor, in particular an internal combustion engine, and which is driven by gear elements, in the manner of a pump distributor gear, acts on at least two hydraulic pumps and has at least one further gear which acts directly on an output member of a power shift transmission, wherein at least in the region of the gear at least one coupling element is positioned, and wherein the power shift at least one of at least a, drivable in the hydrostatic circuit shaft has, in the area of which clutches, brakes, components of a single-stage planetary gear and the like components are provided, wherein the output element of the Lastsch old gear is connected to at least one output shaft.
- the object of the subject invention is to provide an alternative hydrostatic mechanical power split transmission which is suitable
- CONFIRMATION COPY To operate internal combustion engines speed optimized and at the same time to achieve improved efficiencies that are activated in different operating conditions via couplings those drive elements that justify an optimal efficiency balance and by such drives are switched off and stopped by clutches such drive elements that are not functionally used in certain operating areas but could degrade the overall efficiency, eg by drag loss of hydraulic motors.
- a hydrostatic mechanical branching transmission comprising a housing, at least one, consisting of at least one hydraulic pump and at least one hydraulic motor first power branch, at least one disposed within the housing of at least one Antriebsmötor, in particular an internal combustion engine as a further power branch, medium or directly drivable drive shaft which has gear elements which selectively via either at least one clutch acts either directly or indirectly on the sun gear of a planetary gear or the drive shaft can be decoupled from the planetary gear, the planetary gear depending on the respective operating state of the whoverzweigungsgetnebes over other clutches in a forced run is switchable.
- the transmission according to the invention can be driven directly or indirectly by at least one drive motor, in particular an internal combustion engine, via a drive shaft provided with at least one clutch, which can be switched directly or indirectly either selectively to the sun gear of the planetary gear or selectively non-positively connected, wherein the Planetary gear can be selectively switched over at least two clutches in a forced running.
- the provided in the range of the power split transmission clutches / brakes can be operated so that the transmission either purely hydraulically branched off with disconnected mechanical drive shaft, i. hydraulically driven and with mechanically switched drive shaft purely mechanically with optional forced running of the planetary gear and / or at optional shutdown of the hydrostatic power branch. can be operated.
- a shaft which is advantageously designed as a cardan shaft, can be driven directly by the drive motor.
- the single hydraulic motor can be selectively coupled to the sun gear and / or to the ring gear.
- the hydraulic motor can also be disconnected via corresponding clutches of the planetary gear.
- the subject matter of the invention does not exclude that the hydraulic motor and / or the hydraulic pump can also be positioned outside the housing, provided that the installation conditions within a vehicle, for example a wheel loader, leave this.
- the hydraulic motor and / or the hydraulic pump are arranged inside the housing, it is proposed according to a further idea of the invention to design the hydraulic motor and / or the hydraulic pump without its own housing body.
- the movable drive elements of the Hydraulikmotorsr and / or the hydraulic pump can therefore - be positioned outside a housing oil sump - to avoid churning losses.
- the case of a housing for a hydraulic motor and / or a hydraulic pump necessarily provided drain holes for cooling the movable drive elements are now unnecessary, since oil from the housing oil sump can be used, by means of which the movable drive elements of the housingless hydraulic motor and / or the hydraulic pump are molded. By avoiding churning losses, a considerable increase in the overall efficiency of the power split transmission can be brought about.
- the further (mechanical) power branch can be switched to the sun gear in a power-adaptive and / or speed-adaptive and / or acceleration-adaptive manner via an associated clutch.
- the additional (mechanical) power branch can be switched to the sun gear in such a way that the internal combustion engine can be operated in an optimized manner.
- hydraulic motor is power-adaptive and / or speed-adaptive and / or acceleration-adaptive via a clutch to the sun gear switchable.
- the hydraulic motor is formed by an adjusting motor and the hydraulic pump by a variable displacement pump.
- hydraulic pump is driven directly or indirectly by the drive motor.
- the ring gear of the planetary gear can be fixed via a brake, wherein the web of the planetary gear is medium or directly connected to the output shaft.
- Figures 1 and 2 are schematic diagrams of the hydrostatic mechanical power split transmission according to the invention with different structure of the drive elements.
- FIGS 1 and 2 show schematic diagrams of the power split transmission 1 according to the invention with different structure of the drive elements.
- the power split transmission 1 includes a housing 2, which is mechanically driven via a shaft 8 designed as a drive shaft in this example.
- a trained as an internal combustion engine drive motor 3 thereby drives a drive shaft 4, on which a gear member 5 is directly attached and meshes with a further gear member 24, which in turn drives the shaft 8.
- the gear member 5 is also connected to " a gear 12 in operative connection, wherein the gear elements 5,12, the hydraulic pumps 9 and 14 and designed as a variable displacement hydraulic pump 9 mounted on the power split transmission 1, respectively, the housing 2, designed as an adjustment motor, hydraulic motor 16 drives.
- the hydraulic motor 16 can also be arranged within the housing 2 to reduce the installation space and used in this design as a housing-less hydraulic motor 16.
- the housing 2 there is a planetary gear 31, essentially consisting of ring gear 11, planet 30, sun gear 42 and a web 32. Furthermore, the power split transmission 1, respectively the housing 2, the drive shaft 41 for a hydrostatic Operation via the hydraulic motor 16.
- phase of a first driving range with usually low speeds and high traction or torque demand drives the Hydraulic motor 16 to the sun gear 42, wherein a brake 34 is non-positively connected to clamp the ring gear 11 against the housing 2, while another clutch 29 is opened and a further clutch 43 is closed.
- the hydraulic motor 16 drives the sun gear 42 via the gears 26, 22, so that the toothed wheels 18, 19 drive the output shaft 20 via the web 32.
- the couplings 13 likewise introduced in the power split transmission 1 are opened, so that no mechanical power flow can take place via the shaft 8 or the drive shaft 25, for example a propeller shaft, onto the gear 22 likewise present in the power split transmission 1.
- the power split for optimal speed and / or towneinsteNNung the drive motor 3 is set by the brake 34 and a further clutch 43 is released and the clutch 13 and the clutch 29 are closed.
- the power of the drive motor 3 on the one hand via the mechanical strand drive shaft 4, gear elements 5 and 24, shaft 8 and drive shaft 25, clutch 13 and gear 22 is directed to the sun gear 42 of the planetary gear 31 and on the other hand power of the drive motor 3 is hydrostatic over the hydraulic pump 9 and passed to the hydraulic motor 16, wherein the hydraulic motor 16 now the ring gear 11 via shaft 41, clutch 29, gear 44 and gear 23 drives the power of the mechanical strand and the hydrostatic power are summed in the planetary gear 31 and on the Bridge 32 headed.
- the speeds of the ring gear 11 and the sun gear 42 are in this case added in the manner of a superposition gear and the sum of both speeds results in the planetary gear output speed at the web 32, which determines the speed of the output torque 20 and the resulting Fährzeug für directly proportional.
- the setting of the rotational speed of the ring gear 11 is made via the well-controllable hydraulic motor 16 so that in view of the required vehicle speed, the speed of the sun gear 42 and thus the directly proportional speed of the drive motor 3 in the CVT mode (Contihous Variable Transmission) efficiency - ünd / or optimized performance is set.
- Figure 2 shows another configuration of the drive elements, wherein the driving areas are carried out in the same manner as described in Figure 1.
- a Reversiercut consisting of a gear 35, a clutch 36 and gears 45,37, provided in the region of the drive shaft 25 to selectively change the direction of rotation of the drive shaft.
Abstract
L'invention concerne une transmission hydrostatique mécanique comportant un carter (2), au moins une première branche de puissance constituée d'au moins une pompe hydraulique (9) et d'au moins un moteur hydraulique (16), au moins un arbre d'entraînement (25) agencé à l'intérieur du carter et pouvant être entraîné directement ou indirectement par au moins un moteur d'entraînement, en particulier un moteur à combustion interne (3) représentant une autre branche de puissance, lequel arbre est muni d'éléments de type roue dentée (21, 22) qui agissent de manière sélective directement ou indirectement sur le pignon planétaire (42) d'un engrenage planétaire (31) par l'intermédiaire d'au moins un accouplement (13), ou bien l'arbre d'entraînement peut être désaccouplé de l'engrenage planétaire, l'engrenage planétaire pouvant être commuté en mouvement forcé par l'intermédiaire d'autres accouplements (29, 43) en fonction de l'état de fonctionnement respectif de la transmission à répartition de puissance.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180063655.8A CN103282695B (zh) | 2010-12-30 | 2011-12-20 | 功率分流传动装置 |
EP11833600.7A EP2659165B1 (fr) | 2010-12-30 | 2011-12-20 | Transmission à dérivation de puissance |
US13/995,333 US9109680B2 (en) | 2010-12-30 | 2011-12-20 | Power split gearbox |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010056474 | 2010-12-30 | ||
DE102010056474.5 | 2010-12-30 | ||
DE102011102210.8 | 2011-05-21 | ||
DE102011102210A DE102011102210A1 (de) | 2010-12-30 | 2011-05-21 | Leistungsverzweigungsgetriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012089192A1 true WO2012089192A1 (fr) | 2012-07-05 |
Family
ID=45974191
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2011/002148 WO2012089192A1 (fr) | 2010-12-30 | 2011-12-20 | Transmission à dérivation de puissance |
Country Status (5)
Country | Link |
---|---|
US (1) | US9109680B2 (fr) |
EP (1) | EP2659165B1 (fr) |
CN (1) | CN103282695B (fr) |
DE (1) | DE102011102210A1 (fr) |
WO (1) | WO2012089192A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202015102282U1 (de) | 2015-05-05 | 2015-05-18 | Kessler & Co. Gmbh & Co. Kg | Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe |
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US10670124B2 (en) | 2013-12-31 | 2020-06-02 | Deere & Company | Multi-mode infinitely variable transmission |
US10655710B2 (en) | 2013-12-31 | 2020-05-19 | Deere & Company | Multi-mode infinitely variable transmission that provides seamless shifting |
US10647193B2 (en) | 2014-04-09 | 2020-05-12 | Deere & Company | Multi-mode power trains |
US10738868B2 (en) | 2014-04-09 | 2020-08-11 | Deere & Company | Multi-mode powertrains |
US10037397B2 (en) * | 2014-06-23 | 2018-07-31 | Synopsys, Inc. | Memory cell including vertical transistors and horizontal nanowire bit lines |
DE202015004528U1 (de) * | 2015-04-27 | 2016-07-28 | Liebherr-Components Biberach Gmbh | Arbeitsmaschine mit leistungsverzweigbarem Antrieb |
CN104948681A (zh) * | 2015-06-16 | 2015-09-30 | 潍柴动力股份有限公司 | 一种液压工程机械的变速装置及其变速器、变速方法 |
CN106545637A (zh) * | 2016-10-31 | 2017-03-29 | 广西柳工机械股份有限公司 | 动力分配调节系统及装载机动力系统 |
US10619711B2 (en) | 2017-04-12 | 2020-04-14 | Deere & Company | Infinitely variable transmission with power reverser |
US11052747B2 (en) | 2018-05-04 | 2021-07-06 | Deere & Company | Multi-mode powertrains |
US11091018B2 (en) | 2018-05-11 | 2021-08-17 | Deere & Company | Powertrain with variable vertical drop distance |
US10975959B2 (en) | 2019-04-01 | 2021-04-13 | Deere & Company | Transmission clutch braking control system |
US11137052B2 (en) | 2019-08-29 | 2021-10-05 | Deere & Company | Transmission assembly with integrated CVP |
US11351983B2 (en) | 2019-10-31 | 2022-06-07 | Deere & Company | Power control system with transmission transient boost function |
DE102019132121A1 (de) | 2019-11-27 | 2021-05-27 | Claas Selbstfahrende Erntemaschinen Gmbh | Antriebsstrang für eine landwirtschaftliche Arbeitsmaschine |
US11846085B2 (en) | 2020-02-17 | 2023-12-19 | Deere & Company | Energy management system for a hybrid vehicle with an electrically powered hydraulic system |
CN111306279B (zh) * | 2020-02-21 | 2021-08-03 | 江苏大学 | 一种单泵控双马达机械液压复合传动装置 |
US11325459B2 (en) | 2020-10-09 | 2022-05-10 | Deere & Company | Low profile transmission assembly with integrated CVP |
US11613246B2 (en) | 2021-01-21 | 2023-03-28 | Deere & Company | Power control system with engine throttle shift function |
US11628822B2 (en) | 2021-02-09 | 2023-04-18 | Deere & Company | Power control system with stall prevention clutch modulation function |
US11299141B1 (en) | 2021-02-10 | 2022-04-12 | Deere & Company | System for multi-layer braking and retardation in a work vehicle |
US11820361B2 (en) | 2021-11-30 | 2023-11-21 | Deere & Company | Transmission assembly with electrical machine unit for improved shift quality |
US11585412B1 (en) | 2021-12-22 | 2023-02-21 | Deere & Company | Electronically-variable, dual-path power shift transmission for work vehicles |
US11607948B1 (en) | 2021-12-22 | 2023-03-21 | Deere & Company | Electronically-variable power shift transmission for work vehicles |
US11913528B1 (en) | 2022-10-28 | 2024-02-27 | Deere & Company | Multi-mode continuously variable transmission assembly with drop set arrangement |
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JPS49120075A (fr) * | 1973-11-28 | 1974-11-16 | ||
SU1504113A1 (ru) | 1987-12-21 | 1989-08-30 | Производственное объединение "Минский тракторный завод им.В.И.Ленина" | Бесступенчата передача дл трансмиссии самоходной машины |
JPH0544816A (ja) | 1991-08-09 | 1993-02-23 | Komatsu Ltd | 装輪車両用変速装置 |
DE19747459A1 (de) * | 1997-10-27 | 1999-05-06 | Brueninghaus Hydromatik Gmbh | Hydrostatisch-mechanischer Fahrantrieb |
JP2005114128A (ja) * | 2003-10-10 | 2005-04-28 | Yanmar Co Ltd | 走行作業機における動力伝達装置 |
DE102004001929A1 (de) | 2004-01-14 | 2005-08-04 | Zf Friedrichshafen Ag | Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe |
WO2009071060A2 (fr) | 2007-12-07 | 2009-06-11 | Hytrac Gmbh | Transmission à dérivation de puissance |
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US6565471B2 (en) * | 2000-12-19 | 2003-05-20 | Case Corporation | Continuously variable hydro-mechanical transmission |
JP4275908B2 (ja) * | 2002-08-02 | 2009-06-10 | 株式会社 神崎高級工機製作所 | 走行作業車のセンター差動装置 |
JP4570418B2 (ja) * | 2003-09-16 | 2010-10-27 | 株式会社小松製作所 | 油圧−機械式変速装置の制御装置 |
WO2008103298A1 (fr) * | 2007-02-16 | 2008-08-28 | Deere & Company | Procédé pour contrôler deux unités hydrostatiques à déplacement variable dans une transmission hydromécanique variable à l'infini |
-
2011
- 2011-05-21 DE DE102011102210A patent/DE102011102210A1/de not_active Withdrawn
- 2011-12-20 EP EP11833600.7A patent/EP2659165B1/fr not_active Not-in-force
- 2011-12-20 CN CN201180063655.8A patent/CN103282695B/zh not_active Expired - Fee Related
- 2011-12-20 WO PCT/DE2011/002148 patent/WO2012089192A1/fr active Application Filing
- 2011-12-20 US US13/995,333 patent/US9109680B2/en not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS49120075A (fr) * | 1973-11-28 | 1974-11-16 | ||
SU1504113A1 (ru) | 1987-12-21 | 1989-08-30 | Производственное объединение "Минский тракторный завод им.В.И.Ленина" | Бесступенчата передача дл трансмиссии самоходной машины |
JPH0544816A (ja) | 1991-08-09 | 1993-02-23 | Komatsu Ltd | 装輪車両用変速装置 |
DE19747459A1 (de) * | 1997-10-27 | 1999-05-06 | Brueninghaus Hydromatik Gmbh | Hydrostatisch-mechanischer Fahrantrieb |
JP2005114128A (ja) * | 2003-10-10 | 2005-04-28 | Yanmar Co Ltd | 走行作業機における動力伝達装置 |
DE102004001929A1 (de) | 2004-01-14 | 2005-08-04 | Zf Friedrichshafen Ag | Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe |
WO2009071060A2 (fr) | 2007-12-07 | 2009-06-11 | Hytrac Gmbh | Transmission à dérivation de puissance |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202015102282U1 (de) | 2015-05-05 | 2015-05-18 | Kessler & Co. Gmbh & Co. Kg | Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe |
Also Published As
Publication number | Publication date |
---|---|
EP2659165B1 (fr) | 2014-10-08 |
US9109680B2 (en) | 2015-08-18 |
CN103282695B (zh) | 2017-02-15 |
US20140018201A1 (en) | 2014-01-16 |
DE102011102210A1 (de) | 2012-07-05 |
EP2659165A1 (fr) | 2013-11-06 |
CN103282695A (zh) | 2013-09-04 |
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